Hybrid vehicle and associated control method

CROSS-REFERENCE TO RELATED APPLICATIONS

This application is a continuation-in-part of U.S. application Ser. No. 13/539,945 filed Jul. 2, 2012, now U.S. Pat. No. 8,834,317, the disclosure of which is incorporated in its entirety by reference herein.

TECHNICAL FIELD

This disclosure relates generally to controlling the engine speed and combined output torque of a hybrid vehicle in response to driver inputs.

BACKGROUND

In a vehicle having a discrete ratio transmission, the speed of the transmission input shaft is constrained to be proportional to the vehicle speed with a finite set of ratios, except during the brief interval while the transmission is shifting from one ratio to another ratio. When the torque converter is locked, the engine speed is also constrained to be proportional to vehicle speed. In a hybrid electric vehicle having a power-split architecture, on the other hand, the transmission does not mechanically impose a strict relationship between the engine speed and the vehicle speed.

Even in vehicles with automatic transmissions, in which selection of the gear ratio or engine speed is ordinarily determined by a controller, some drivers prefer to occasionally over-ride the controller to provide operation similar to a manual transmission. Some vehicles are equipped with shift paddles or other driver interface features which permit the driver to signal a desire for a higher or a lower gear ratio relative to the gear ratio automatically selected by the vehicle controller, with an associated change in engine speed and vehicle torque. In a discrete ratio transmission, the controller responds to such a command by shifting to a different one of the discrete gear ratios, which adjusts engine speed accordingly and provides associated torque multiplication at the vehicle wheels. However, in a vehicle with a continuously variable transmission or similar gearbox, such as a power-split hybrid, the response is more complicated because the transmission does not inherently provide discrete gear ratios with associated different torque multiplication.

SUMMARY

In various embodiments, a hybrid vehicle control strategy implements four different operating modes. The vehicle controller determines which operating mode is utilized at any given time in response to operation of various driver interface elements including a shift lever, a downshift selector, and an upshift selector, for example. In two of the operating modes, the controller permits the driver to select a virtual gear that impacts the engine speed and the combined output torque of the engine and one or more traction motors. The controller can utilize different logic for shutting the engine off and driving solely with electric power depending on which operating mode is active.

In one embodiment, a method of controlling a hybrid vehicle includes controlling an engine and a traction motor in an automatic mode and then increasing the wheel torque to transition to a select shift mode. In the automatic mode, the wheel torque is based on pedal position and vehicle speed. In the select shift mode, the wheel torque is based on a driver modifiable virtual gear number in addition to pedal position and vehicle speed. In the select shift mode, the wheel torque decreases as the virtual gear number increases. The method may include increasing the virtual gear number in response to operation of an upshift selector and decreasing the virtual gear number in response to operation of a downshift selector. The transition to select shift mode may be initiated by operation of the downshift selector. When transitioning to the select shift mode, the method may include selecting the highest initial virtual gear number that will result in a torque increase.

In another embodiment, a controller for a hybrid vehicle includes input communication channels, output communication channels, and control logic. The input communication channels receive input signals indicating vehicle speed, position of a driver operated accelerator pedal, driver operation of a downshift selector, and driver operation of an upshift selector. The output communication channels send control signals to an engine and at least one traction motor. The control logic is configured to control the engine and traction motor(s) in an automatic mode and then increasing the wheel torque to transition to a select shift mode. In the automatic mode, the wheel torque is based on pedal position and vehicle speed. In the select shift mode, the wheel torque is based on a driver modifiable virtual gear number in addition to pedal position and vehicle speed. In the select shift mode, the wheel torque decreases as the virtual gear number increases. The controller may increase the virtual gear number in response to operation of an upshift selector and decrease the virtual gear number in response to operation of a downshift selector. When transitioning to the select shift mode, the controller may select the highest initial virtual gear number that will result in a torque increase.

In another embodiment, a hybrid vehicle includes a planetary gear set and a controller. The elements of the planetary gear set, which include a sun gear, a ring gear, and a planet carrier, are drivably connected to an engine, a set of driving wheels, and a first electric machine. A second electric machine is drivably connected to the wheels. The controller is configured to control the engine and the electric machines in an automatic mode and then increasing the wheel torque to transition to a select shift mode. In the automatic mode, the wheel torque is based on pedal position and vehicle speed. In the select shift mode, the wheel torque is based on a driver modifiable virtual gear number in addition to pedal position and vehicle speed. When transitioning to the select shift mode, the controller may select the highest initial virtual gear number that will result in a torque increase.

Various embodiments according to the present disclosure can provide one or more advantages. For example, systems and methods for controlling a hybrid vehicle according to the present disclosure mimic or emulate a manual or select shift mode of an automatic step-ratio transmission in a hybrid vehicle having a continuously variable transmission or similar gearbox. In addition, various strategies of the present disclosure provide drivers of hybrid vehicles more interactive controls to manually command powertrain speed and acceleration to provide enhanced luxury features and a sporty feel.

The above advantages and other advantages and features will be readily apparent from the following detailed description of the preferred embodiments when taken in connection with the accompanying drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

<figref idref="DRAWINGS">FIG. 1</figref> is a schematic diagram illustrating a vehicle powertrain, controller, and user interface features of a representative embodiment of a hybrid vehicle according to the present disclosure;

<figref idref="DRAWINGS">FIG. 2</figref> is a state transition chart illustrating operation of a system or method of an embodiment of the present disclosure;

<figref idref="DRAWINGS">FIG. 3</figref> is a flow chart illustrating operation of a system or method according to various embodiments when in a Normal operating mode;

<figref idref="DRAWINGS">FIG. 4</figref> is a graph illustrating a relationship between vehicle speed, accelerator pedal position, and wheel torque command of a representative embodiment according to the disclosure;

<figref idref="DRAWINGS">FIG. 5</figref> is a graph illustrating a relationship between vehicle speed, target engine power, and engine speed command of a representative embodiment according to the disclosure;

<figref idref="DRAWINGS">FIG. 6</figref> is a flow chart illustrating operation of a system or method according to various embodiments when in the Live-In-Drive (LID) operating mode;

<figref idref="DRAWINGS">FIG. 7</figref> is a graph illustrating a relationship between actual accelerator pedal position, virtual gear number or operating mode, and modified pedal position of a representative embodiment according to the disclosure;

<figref idref="DRAWINGS">FIG. 8</figref> is a graph illustrating a relationship between vehicle speed, virtual gear number, and engine power clipping limit of a representative embodiment according to the disclosure;

<figref idref="DRAWINGS">FIG. 9</figref> is flow chart illustrating operation of a system or method according to embodiments of the disclosure when in the Sport operating mode;

<figref idref="DRAWINGS">FIG. 10</figref> is a flow chart illustrating operation of a strategy for shutting off and restarting the engine in certain operating modes of various embodiments of the disclosure; and

<figref idref="DRAWINGS">FIG. 11</figref> is a flow chart illustrating operation of a system or method when in the SST operating mode according to various embodiments of the disclosure.

DETAILED DESCRIPTION

As required, detailed embodiments of the present invention are disclosed herein; however, it is to be understood that the disclosed embodiments are merely exemplary of the invention that may be embodied in various and alternative forms. The figures are not necessarily to scale; some features may be exaggerated or minimized to show details of particular components. Therefore, specific structural and functional details disclosed herein are not to be interpreted as limiting, but merely as a representative basis for teaching one skilled in the art to variously employ the present invention.

A powertrain for a hybrid electric vehicle is illustrated schematically in <figref idref="DRAWINGS">FIG. 1</figref>. The powertrain includes an internal combustion engine <b>20</b> driveably connected to a planet carrier <b>22</b>, a generator <b>24</b> driveably connected to a sun gear <b>26</b>, and an output shaft <b>28</b> driveably connected to a ring gear <b>30</b>. Elements are driveably connected when there is a mechanical power flow path between them such that the speeds of the elements are constrained to be substantially proportional. Planet carrier <b>22</b> supports a set of planet gears <b>32</b> such that each planet gear is in continuous meshing engagement with sun gear <b>26</b> and ring gear <b>30</b>. Output shaft <b>28</b> drives the vehicle wheels directly or indirectly, such as via a differential assembly, for example.

Traction motor <b>34</b> is driveably connected to the output shaft <b>28</b>. Both the generator <b>24</b> and the traction motor <b>34</b> are reversible electrical machines that are capable of converting electrical power into rotational mechanical power or converting rotational mechanical power into electrical power. The terms generator and motor should be regarded merely as labels for ease of description and does not limit the function or operation of either electrical machine. Generator <b>24</b> and traction motor <b>34</b> are both electrically connected to battery <b>36</b>.

The rotational speed of sun gear <b>26</b>, carrier <b>22</b>, and ring gear <b>30</b> are linearly related such that the speed of carrier <b>22</b> is a weighted average of the speed of sun gear <b>26</b> and ring gear <b>30</b>. Consequently, the speed of the engine <b>20</b> is not constrained to be proportional to the speed of the output shaft <b>28</b> in this arrangement. Instead, the engine speed can be selected or controlled independently of the vehicle speed by setting the generator speed accordingly. Power flows from the engine to the output shaft through a combination of mechanical power transfer and electrical power transfer. During some operating conditions, the engine <b>20</b> can generate more power than what is delivered to the output shaft <b>28</b> with the difference, neglecting efficiency losses, delivered to battery <b>36</b>. Under other operating conditions, the battery <b>36</b> in combination with generator <b>24</b> and/or traction motor <b>34</b> can supplement the power delivered by the engine <b>20</b> such that more power is delivered to the output shaft <b>28</b>.

The engine <b>20</b>, generator <b>24</b>, and traction motor <b>34</b>, all respond to control signals from controller <b>38</b>. These control signals determine the amount of torque generated. The controller also receives speed signals from the engine <b>20</b>, generator <b>24</b>, and traction motor <b>34</b> and a state of charge signal from battery <b>36</b>. The controller accepts input signals indicating driver intention from a brake pedal <b>40</b>, an accelerator pedal <b>42</b>, a shift lever <b>44</b>, a steering wheel <b>46</b>, a downshift selector <b>48</b>, an upshift selector <b>50</b>, and a cruise control button <b>51</b>. Shift lever <b>44</b> allows the driver to select Park, Reverse, Neutral, Drive, and Sport driving modes. The upshift and downshift selectors may, for example, be paddles mounted on opposite sides of the steering wheel. Other upshift and downshift selector implementations, such as additional positions of the shift lever, are known and are suitable for use with the present invention.

In certain operating modes, the engine speed may vary continuously in response to changes in accelerator pedal position as opposed to varying through discrete shift events. This terminology should not be construed to preclude use of a digital controller which manipulates a large but finite number of control signal levels at frequent time intervals.

The top level control states are illustrated in <figref idref="DRAWINGS">FIG. 2</figref>. The controller starts in state <b>60</b> and transitions to Normal mode <b>62</b> as soon as the driver selects the Drive (D) position using shift lever <b>44</b>. Operation in Normal mode is illustrated by the flow diagram of <figref idref="DRAWINGS">FIG. 3</figref>. In Normal mode, the controller repeatedly performs the operations of setting the output torque <b>66</b>, setting the engine mode <b>68</b>, setting the engine power <b>69</b>, and setting the engine speed <b>70</b>. In Normal mode, the target output torque is calculated at step <b>66</b> based on accelerator pedal position and vehicle speed using a table such as that illustrated in <figref idref="DRAWINGS">FIG. 4</figref>. Vehicle speed can be calculated from traction motor speed or wheel speed sensors. Engine mode is set to either running or stopped at step <b>68</b> using a variety of input signals including battery state of charge, output power command, accelerator pedal position, and vehicle speed. If the engine mode is running, a target engine power and target engine speed is calculated at steps <b>69</b> and <b>70</b> to minimize fuel consumption while delivering the desired output torque and maintaining the battery at a desired state of charge. If the battery state of charge is near a target level, then the target engine power is set equal to the power that is to be delivered to the wheels which can be computed from the target wheel torque and the vehicle speed. If the battery state of charge is low, the target engine power is set higher to generate additional power to charge the battery. If the battery state of charge is high, the target engine power is set lower to conserve fuel. The target engine speed is computed based on target engine power and vehicle speed using a table such as that illustrated in <figref idref="DRAWINGS">FIG. 5</figref>. Finally, operating parameters of the engine, generator, and traction motor are adjusted such that the actual output torque and engine speed tend toward the selected targets.

Referring again to <figref idref="DRAWINGS">FIG. 2</figref>, the controller transitions from Normal mode <b>62</b> to Live-In-Drive (LID) mode <b>72</b> whenever the driver activates the downshift selector <b>48</b>. LID mode permits the driver to influence the engine speed and wheel torque by selecting a virtual gear number. Operation in LID mode is illustrated by the flow diagram of <figref idref="DRAWINGS">FIG. 6</figref>. Upon entering LID mode, the controller selects an initial virtual gear ratio at step <b>74</b> and then repeatedly performs the operations of setting the output torque at steps <b>76</b> and <b>66</b>′, setting the engine power and engine speed at steps <b>69</b>′ and <b>78</b>, and updating the virtual gear ratio in steps <b>80</b> and <b>82</b>. Each of these operations is discussed in additional detail below. As shown in <figref idref="DRAWINGS">FIG. 2</figref>, a number of conditions cause the controller to transition back to Normal mode <b>62</b>, including vehicle speed dropping below a low threshold value or an automatically selected downshift. Additionally, a transition can be triggered when the controller detects a cruising condition, as indicated by activation of the cruise control <b>51</b>, or a tip-out condition, indicated by a reduction in accelerator pedal position, and the condition persists for some predetermined amount of time. This latter type of condition will not result in a transition, however, if the controller detects a high driver workload at step <b>84</b>, such as might be indicated by large displacements of steering wheel <b>46</b>, large yaw, pitch, or roll rates, or high longitudinal or lateral accelerations, for example.

At step <b>76</b>, a modified accelerator pedal position is calculated from the measured accelerator pedal position using a table such as illustrated in <figref idref="DRAWINGS">FIG. 7</figref>. This modified accelerator pedal position is used in place of the actual pedal position in step <b>66</b>′ to calculate the target output torque. The curves in <figref idref="DRAWINGS">FIG. 7</figref> are selected to simulate the output torque capability of a powertrain with a discrete ratio transmission. Specifically, as the virtual gear number (1^stthrough 8^thin this example) increases, the resulting target output torque is lower for any given non-zero accelerator pedal position. The combined effect of steps <b>76</b> and <b>66</b>′ is operation of the engine and at least one traction motor such that combined output torque corresponds to one of a plurality of output torque functions, each output torque function having a distinct output torque at a maximum value of accelerator pedal position for an associated vehicle speed.

The initial virtual gear is selected at step <b>74</b>. The operating point with respect to <figref idref="DRAWINGS">FIG. 7</figref> is along line <b>236</b> prior to the transition. The controller selects virtual gear number corresponding to the next higher curve from among curves <b>240</b>-<b>254</b>. In other words, the controller selects a virtual gear number based on the current actual pedal position such that, in the selected virtual gear the modified pedal position is higher than the actual pedal position, but the modified pedal position would be less than the actual pedal position in the next higher virtual gear. For example, if the operating point before the transition is point <b>258</b>, 4^thgear would be selected such that the operating point becomes point <b>260</b>. This has the effect of ensuring that wheel torque increases upon transitioning from Normal mode to LID mode at constant accelerator position.

As also shown in <figref idref="DRAWINGS">FIG. 6</figref>, in LID mode <b>72</b>, the target engine power is calculated at step <b>69</b>′ and target engine speed is calculated at step <b>78</b>. At step <b>78</b>, the controller first calculates a clipping limit for the engine power based on the vehicle speed and the currently selected virtual gear number using a table such as illustrated in <figref idref="DRAWINGS">FIG. 8</figref>. For example, if the current virtual gear number is 4, the clipping limit would be set according to curve <b>268</b>. If the clipping limit is higher than the target engine power, then the clipping limit is used in place of the target engine power to calculate the target engine speed. When the clipping limit is used, engine speed is set higher in lower virtual gear numbers than it would be set in higher virtual gear numbers. Also, when the clipping limit is used, the target engine speed does not vary as accelerator pedal position varies. When the clipping limit is less than the target engine power, which would be most likely when a high virtual gear number is selected, then the target engine speed is the same in LID mode as it would be in Normal mode. The clipping limit does not impact the commanded engine power which is adjusted to deliver the target wheel torque.

As also shown in <figref idref="DRAWINGS">FIG. 6</figref>, in step <b>80</b>, the controller checks for activations of either the upshift selector or the downshift selector and adjusts the virtual gear number accordingly. In step <b>82</b>, the controller determines if there is a need to automatically adjust the virtual gear number. In particular, an upshift can be triggered by an increase in vehicle speed. Similarly, a downshift can be indicated when vehicle speed decreases. However, as mentioned previously, the controller transitions back to Normal mode <b>62</b> when an automatic downshift is indicated. In this embodiment, the automatic shift criteria are calibrated such that automatic changes in virtual gear number are generally less common than shifts in a traditional discrete ratio automatic transmission.

Referring once again to <figref idref="DRAWINGS">FIG. 2</figref>, the controller transitions from Normal mode <b>62</b> to Sport mode <b>94</b> whenever the driver moves the shift lever <b>44</b> to the Sport (S) position. Operation in Sport mode is illustrated by the flow diagram of <figref idref="DRAWINGS">FIG. 9</figref>. The controller repeatedly performs the operations of setting the output torque <b>96</b> and <b>66</b>″, setting the engine speed <b>99</b>, and setting the engine mode <b>98</b>. To provide a more sporty reaction to accelerator pedal movements, the target output torque is computed based on a modified accelerator pedal position as illustrated by the upper heavy line <b>238</b> in <figref idref="DRAWINGS">FIG. 7</figref>. The mapping between actual accelerator pedal position and modified accelerator pedal position is selected such that the value is equal at the minimum <b>237</b> and maximum <b>239</b> values, but the modified value is higher for all intermediate levels.

As also shown in <figref idref="DRAWINGS">FIG. 9</figref>, target engine speed is set in step <b>99</b> using a similar algorithm to that used in Normal mode. However, the target engine speed is scaled up by a designated amount, such as 10-20% for example, relative to the value that would be used in Normal mode. Unlike the algorithm for setting engine mode used in Normal mode, the algorithm used in Sport mode as indicated at step <b>98</b> only stops the engine when the vehicle is stationary and the brake pedal is depressed. The modified engine mode setting algorithm is illustrated in <figref idref="DRAWINGS">FIG. 10</figref>. If the engine is currently stopped <b>100</b>, then the engine is restarted at step <b>102</b> if the vehicle is moving <b>104</b> or the brake pedal is released <b>106</b>. Similarly, if the engine is currently running, then the engine is stopped at step <b>108</b> only if the vehicle is stationary <b>110</b> and the brake pedal is pressed <b>112</b>.

If the driver activates either the upshift or downshift selector while in Sport mode <b>94</b>, the controller transitions to Select Shift Transmission (SST) mode <b>114</b>, as shown in <figref idref="DRAWINGS">FIG. 2</figref>. In SST mode, the target engine torque and target engine speed are set based on the virtual gear number, as described with respect to LID mode. However, the controller will remain in SST mode until the driver indicates a desire to leave this mode by either holding a shift selector <b>48</b> or <b>50</b> for several seconds of by moving shift lever <b>44</b> back to the Drive (D) position. Operation in SST mode is illustrated by the flow diagram of <figref idref="DRAWINGS">FIG. 11</figref>. The initial virtual gear number is set at step <b>74</b>′ using an analogous method to that used when entering LID as described above except that the initial operating point is along curve <b>238</b> in <figref idref="DRAWINGS">FIG. 7</figref> instead of curve <b>236</b>. Therefore, the controller selects the highest virtual gear number for which the modified pedal position is higher than it would be in Sport mode. This ensures an increase in wheel torque upon transitioning into SST mode. In SST mode, the virtual gear number is adjusted at step <b>80</b>′ in response to activation of downshift selector <b>48</b> and upshift selector <b>50</b> in the same manner as in LID mode. In addition, the controller can automatically adjust the virtual gear number, either up or down, in response to changes in vehicle speed or accelerator pedal position. This automatic feature sets the virtual gear number to 1st gear as the vehicle comes to a stop. However, the driver can override this selection by manipulating the shift selectors while the vehicle is stationary in step <b>118</b>. In SST mode, the engine mode depends on the virtual gear number, vehicle speed, and accelerator pedal position. In step <b>120</b>, the controller calculates an engine shutdown limit, which is an accelerator pedal position below which electric drive is enabled. The shutdown limit is a function of output power demand, virtual gear number, and vehicle speed. The shutdown limits for several gear ratios at a particular vehicle speed and output power demand are illustrated by black circles in <figref idref="DRAWINGS">FIG. 7</figref>. When one of the higher virtual gear numbers, i.e. 5th-8th, is active and the accelerator pedal position is less than the shutdown limit, the normal engine mode algorithm <b>68</b>′ of Normal mode is used. If a lower virtual gear number, i.e. 1st-4th, is active, or if the accelerator position is above the engine shutdown limit, then the more restrictive algorithm <b>98</b>′ of Sport and LID modes is used.

As illustrated by the representative embodiments described above, various embodiments according to the present disclosure can provide one or more advantages, such as emulating a manual or select shift mode of an automatic step-ratio transmission in a hybrid vehicle having a continuously variable transmission or similar gearbox. In addition, various strategies of the present disclosure provide drivers of hybrid vehicles more interactive controls to manually command powertrain speed and acceleration to provide enhanced luxury features and a sporty feel.

While exemplary embodiments are described above, it is not intended that these embodiments describe all possible forms of the invention. Rather, the words used in the specification are words of description rather than limitation, and it is understood that various changes may be made without departing from the spirit and scope of the invention. Additionally, the features of various implementing embodiments may be combined to form further embodiments of the invention. While various embodiments may have been described as providing advantages or being preferred over other embodiments with respect to one or more desired characteristics, as one skilled in the art is aware, one or more characteristics may be compromised to achieve desired system attributes, which depend on the specific application and implementation. These attributes include, but are not limited to: cost, strength, durability, life cycle cost, marketability, appearance, packaging, size, serviceability, weight, manufacturability, ease of assembly, etc. The embodiments described herein that are described as less desirable than other embodiments or prior art implementations with respect to one or more characteristics are not outside the scope of the disclosure and may be desirable for particular applications.